The invention relates to a valve for the temperature-dependent control of at least one hydraulic load, comprising a valve housing having at least one tank connection, at least one working connection and at least one supply connection, a control piston for controlling said connections, which control piston is movably disposed in the valve housing and preloaded by an energy store, such as a working spring, and a thermal element, which can be supplied with a fluid at a specifiable temperature, and which is actively coupled with the control piston. Furthermore, the invention relates to a hydraulic system, which contains at least one such valve.
Energy is converted and transported in hydraulic systems and losses occur in this conversion of energy and transport of energy. As such, mechanical and hydraulic energy is thereby converted into heat. The object of a cooling device is to dissipate this heat from the hydraulic system. The fan of a cooling device can typically be driven hydraulically, wherein the hydraulic drive unit for an allocated hydraulic motor may be designed as a separate circuit, which is independent of the circuit of the fluid that is to be cooled.
A valve of the above mentioned type is known from the subsequently published DE 10 2012 008 480.3. The known valve is used to actuate a hydraulic drive of a fan as a function of the temperature of the fluid that is to be cooled, or more precisely, to predetermine the speed of the fan. The valve and the fan drive, which is actuated by said valve, are disposed in a joint hydraulic circuit. There is still room for improvement in the use of the known valve in sluggish hydraulic systems having more limited adjustment dynamics. In addition, it would be desirable to limit the control pressure predetermined by the valve and thus to be able to protect the thermal element against overloads.
The object of the invention is to expand the area of application for the valve, in particular to include sluggish hydraulic systems having more limited adjustment dynamics, and to make additional functions available to the valve in order to improve the manner in which said valve operates.
This object is achieved according to the invention by a valve having the features of Claim 1 in its entirety.
Accordingly, the invention provides that the thermal element and the control piston are two separate components, which may be disposed in the valve housing in a joint fluid chamber. The fluid, for example a medium that is to be cooled, flows onto, about or through the thermal element, also referred to as the thermal working element, and takes on the temperature of said element. As the temperature of the fluid increases, the thermal element causes a movement, compression or expansion, of the energy store and accordingly, a change in the initial load thereon, which predetermines the pressure that is to be regulated by the control piston, also referred to as the main control piston. By using the energy store, which is typically designed as a compression spring, thus as a working spring, it is possible to use a valve according to the invention, in particular, for the regulation of sluggish hydraulic systems having more limited adjustment dynamics. However, it is absolutely possible to use the solution according to the invention for highly dynamic applications as well.
In a preferred embodiment of the valve according to the invention, a choke piston, which can be moved in the valve housing, is disposed between the thermal element and the control piston, which choke piston is, in particular, connected to the thermal element in an operative connection on the one side, preferably via an actuating element, and is connected to the energy store in an operative connection on the other side, wherein the energy store is in an operative connection with the control piston at the end of said energy store that faces away from the choke piston and in particular, wherein said energy store is connected thereto. An actuating element, for example a push rod, is advantageously formed on the thermal element, which actuating element generates a movement, which is to say, a movement in a working direction, also referred to as an travel distance, with a simultaneous increase of force at the choke piston as the temperature of the fluid increases. Stated more precisely, the actuating element advantageously rests against the choke piston and moves said piston in accordance with the temperature-dependent travel distance thereof. The travel distance and the associated force are transferred to the energy store via the choke piston.
In addition, it is advantageous that a P-T fluid connection is formed in the valve housing from the supply connection to the tank connection, which fluid connection can be controlled by the choke piston, and that the choke piston closes or at least partially opens the P-T fluid connection in accordance with a travel distance of the thermal element. The choke piston opens an increasing choke cross section from the supply connection to the tank connection over the travel distance, or in other words, over the movement of the thermal element. A P-A fluid connection from the supply connection to the working connection, at which the operating pressure that is to be regulated prevails, is typically formed on the control piston, which serves as the main control piston.
In a further preferred embodiment of the valve according to the invention, at least one input choke is provided, which is allocated to the supply connection, and which is preferably disposed in at least one fluid arm in the valve housing that is allocated to the supply connection. The pressure differential across the input choke is increased in accordance with an increasing choke cross section of the choke piston, and the system pressure in the hydraulic system allocated to the hydraulic load must increase disproportionately in order to maintain a balance of forces at the control piston. For this reason, what is actually a linear pressure-temperature characteristic curve can be adapted to the required characteristic curve of a load, for example, a disproportionately increasing characteristic curve of a fan, such as the cube thereof.
In addition, it is advantageous that the thermal element be in an operative connection with an overload element, such as an overload spring, preferably with a compression spring, at the end of said element that is facing away from the control piston and, in particular, that said thermal element be connected thereto, wherein the overload element limits the initial load or, respectively, the force applied to the control piston via the energy store. In this way, a kind of pressure limitation is implemented in such a way that, in the case of a system pressure that exceeds the maximum allowable value, the control piston is brought into full contact with the thermal element via the choke piston, and the pressure that is to be regulated exerts a force on the overload element at the thermal element. The pressure that is to be regulated is limited to the value that is predetermined by the overload element and as a result, the thermal element is protected against an overload.
With respect to the design of the control piston of the valve, the configuration is advantageously provided in such a way that the control piston has a main piston component and a second piston component as differential pistons on a joint piston rod, said piston components having a different effective piston surface as compared to the main piston component, between which a first fluid chamber is delimited, into which the supply connection discharges, wherein the main piston component controls the outlet cross-section between the first fluid chamber and the working connection with control edges or control notches.
In addition, a connection line from the first fluid chamber to the choke piston, as well as a branch line, which runs from said choke piston to the tank connection, may also be present in the valve housing, wherein the fluid passage between the connection line and the branch line can be controlled by means of the choke piston.
In addition, when a fluid path is formed between external fluid ports in the valve housing for the fluid, which fluid defines the temperature at the thermal element, and when the thermal element is disposed in this fluid path, this gives rise to the possibility that the valve can operate self-sufficiently, which is to say, without external fluid lines. In addition, it is advantageous that a fluid return that runs from the thermal element to the tank connection be provided, which preferably also runs in the valve housing. The fluid feed and the fluid return form a kind of internal flushing fluid channel for subjecting the thermal element to a thermal load.
Alternatively, a fluid path may be formed between external fluid connections in the valve housing for the fluid, which fluid defines the temperature of the thermal element, wherein the thermal element is disposed in the fluid path. In the case of this alternative, use is made of an external fluid port, wherein the fluid or, respectively, the flushing fluid is not returned internally via the valve or, respectively, pump housing, but instead, is returned externally.
Regardless of the way in which the application of the fluid or, respectively, the application of the thermal load to the thermal element is configured, at least one external fluid port, which is allocated to the thermal element, may be formed in the valve housing.
According to Claim 10, the invention also relates to a hydraulic system having at least one hydraulic load and at least one valve according to the invention for the temperature-dependent control of the at least one hydraulic load, which is connected to the working connection of the valve, wherein the control piston at least partially opens or closes a P-A fluid connection from the supply connection to the working connection according to the temperature of the thermal element.
As such, at least one hydraulic load may be allocated to a hydraulic motor, which, together with a variable displacement pump, forms a hydraulic system, in particular a motor pump unit, wherein the respective hydraulic load influences the displacement volume of the variable displacement pump, and in particular, predetermines the swivel angle thereof, preferably via a back coupling of the operating pressure. In the preferred hydraulic system according to the invention, a temperature-dependent control of the hydraulic motor and, as a result, the motor power thereof, is implemented. Due to the function-related use of at least one or, advantageously, a plurality of springs, especially preferably, compression springs connected in series, a temperature-dependent regulation of a sluggish hydraulic system having more limited adjustment dynamics is achieved. In this embodiment of the hydraulic system according to the invention, the corresponding hydraulic load is advantageously designed as a actuating cylinder, which is connected to the working connection of the valve on the working side, and wherein the piston of said actuating cylinder predetermines the pivot angle of the variable displacement pump.
In a further preferred embodiment of the hydraulic system according to the invention, the hydraulic motor drives a fan of a cooling device having a fan speed, which is predetermined by the hydraulic system.
As such, according to the invention, an axial piston pump having an integrated temperature control valve is provided as a fan drive without the use of electrical or electronic components.
Further advantages and features of the invention will become apparent from the Figures and the subsequent description of the drawings. According to the invention, the above-specified features and the features presented below may be implemented individually, or in any combination thereof. The features depicted in the Figures are purely schematic, and are not to be understood as being to scale. Shown are:
FIG. 1 a sectional view of an exemplary embodiment of the valve according to the invention, as well as a symbolic depiction of a hydraulic system associated therewith, wherein the system is depicted in the active operating state in which the fluid is in a cold state;
FIG. 2 a travel distance-temperature graph of a thermal element as part of the valve according to the invention;
FIG. 3 a system pressure-temperature graph of a valve according to the invention:
FIG. 4 a more simplified schematic view as compared to FIG. 1, which shows the first exemplary embodiment in the inactive operating state;
FIG. 5 a depiction corresponding to the depiction in FIG. 4, which shows the active operating state, in which the fluid that is to be cooled is warm;
FIG. 6 a depiction corresponding to the depictions in FIGS. 4 and 5, which shows the operating state of the pressure cut-off in the event of an overload;
FIG. 7 in part, a section view, and in part, a symbolic depiction of a second exemplary embodiment of the valve according to the invention, wherein the inactive operating state is shown;
FIG. 8 a more simplified schematic view as compared to FIG. 7 of the second exemplary embodiment, wherein the active operating state in which the fluid is cold is depicted;
FIG. 9 a corresponding depiction of the second exemplary embodiment, wherein the active operating state in which the fluid that is to be cooled is warm is shown, and
FIG. 10 a corresponding depiction of the second exemplary embodiment, wherein the operating state is depicted having a pressure cut-off in the event of an overload.
FIG. 1 shows, shows, in part, a section view, and in part, a symbolic depiction of a first exemplary embodiment of the valve solution according to the invention. The valve, which is designated as a whole as 10, has a valve housing 12, which is made up of three parts 14, 16 and 18, which allow a practical assembly of the valve housing 12 along corresponding separation points 20, which extend vertically. With respect to a simplified depiction, the connectivity solution is not shown in detail. As viewed looking towards the valve 10 according to FIG. 1, a supply or pump connection P, a working connection or utility connection A, as well as a tank connection T are located on the underside of the valve housing 12, which tank connection has a tank or ambient pressure.
In addition, two fluid ports 22, 24 are present on the left side of the valve housing part 16 as viewed in the direction shown in FIG. 1, through which fluid connections a fluid, for example in the form of a hydraulic oil, can flow in the direction indicated by the arrow.
Two fluid chambers 26, 28, which are disposed one behind the other, are present within the valve housing part 18 in the longitudinal direction thereof. A control piston 30, which can be movably guided in a longitudinal direction, is present in the two fluid chambers 26, 28 and within the inner surface of the valve housing 12. According to the depiction in FIG. 1, three piston components 34, 36 and 38 are present on the piston rod 32 of said control piston, which piston components are spaced apart from one another in an axial direction, and are wider than the piston rod 32. The two annular or cylindrically-shaped piston components 34, 36 have the same outer circumference, whereas the piston component 38, by contrast, has a diameter that is reduced accordingly, so that said component is able to move in the fluid chamber 28, the outer circumference of which chamber is likewise reduced accordingly with respect to the fluid chamber 26. The fluid chamber 28 forms a kind of spring chamber, in which an energy store in the form of a compression spring 40 is held. The solution according to the invention may also have no need of the compression spring 40.
According to the depiction in FIG. 1, while the right side of the piston rod 32 projects axially over the piston component 38, in this respect, said piston rod forms a stop surface 39 at the free front surface thereof for possible contact with the aligned inner surface of the valve housing 12 at this location. On the opposite side, however, the piston rod 32 transitions directly into the piston component 34, wherein, according to the depiction in FIG. 1, which corresponds to the valve solution in a cold operating state, said piston component rests against a limit stop 42, which is designed in such a way that a further fluid chamber 44 is formed, having a smaller diameter than the adjacent fluid chamber 26, so that in this respect, there is a sudden change in diameter in the valve housing part 16, which forms a step with respect to the valve housing part 18 at the specified separation point 20, which extends vertically, which separation point serves as a limit stop 42 for the entire control piston 30 insofar as said control piston is located in the left stop position thereof as shown in FIG. 1.
A further piston component 46 adjoins the left piston component 34 of the control piston 30, which piston component is reduced in diameter accordingly with respect to piston component 30 such that it can be movably guided in a longitudinal direction in the additional fluid chamber 44. In the exemplary embodiment presently shown, the additional piston component 46 is an integral component of the piston component 30 and is reduced in diameter along a step 20; it would also be conceivable for the piston rod 32 to carry through, and for the two piston components 38 and 46 to be designed such that they are integral to one another. As viewed in the direction shown in FIG. 1, the additional piston component 46 has a stop element 48 on the left side thereof, which can be brought into abutment with a stop surface on the front surface of a choke piston, which is designated as 50 as a function of the movement positions of the piston assembly within the valve housing. The choke piston 50 can be movably guided in a longitudinal direction within the fluid chamber 44 and has two annular piston components 52, 54, which, as viewed in the axial direction, are held spaced apart from one another via a piston rod component 56, which is disposed therebetween. Such a choke piston 50 is preferably integrally formed.
When the valve assembly, which is shown in FIG. 1, is in the cold operating state, the choke piston 50 rests with the free front surface of the left piston 52 thereof against an additional limit stop 58, which, in turn, is created by a reduction in diameter of said choke piston, produced by a fourth fluid chamber 60, which, as viewed in the axial direction of the piston assembly, is delimited on the right side thereof by the front surface of the piston component 52 of the choke piston 50, and which is delimited on the other, opposite side thereof by a thermal element 62. Furthermore, an actuating element 64 passes through the fourth fluid chamber 60, as viewed in the axial direction of the valve 10, which actuating element is associated with a thermal element 62.
The thermal element 62 is received in an element receptacle 66 within the valve housing part 16; however, the thermal element 62 is able to move, contrary to the action of an additional energy store in the form of an additional compression spring 68, to the left, as viewed in the direction shown in FIG. 1, as a function of the operating state of the valve 10, wherein the thermal element 62 is then spaced at the right, front end surface thereof at a distance from a stop surface 70, which will be described in greater detail below. Otherwise, the additional compression spring 68 is supported at one free end thereof on the thermal element 62, and at the other free end thereof on the interior of the valve housing part 14, which closes off the valve housing 12 from the outside in the manner of an end cap. In addition, the thermal element 62 is enclosed by an annular chamber 72, into which the fluid ports 22, 24 discharge.
An additional, third energy store in the form of a compression spring extends between the choke piston 50 and the additional piston component 46, which third energy store is designated in the following as the working spring 74. As is further made clear in FIG. 1, the supply or pump connection P as well as the working connection A discharge at least in part into the first fluid chamber 26, which is delimited at the edges thereof by the two piston components 36, 38. The tank connection T, in turn, discharges into the first fluid chamber 26 in the region between the two piston components 34 and 36 of the control piston 30. A connection line 76 discharges between that part of the first fluid chamber 26, which extends between the two piston components 36 and 38, which connection line extends through the valve housing 12 in the upper region thereof in a longitudinal direction, and which discharges, with the other end thereof, into the third fluid chamber 44 and does so in that region, which is delimited by the two piston components 52 and 54 of the choke piston 50. However, depending on the structural configuration, the connection line 76 may, instead, be disposed in a rear region (not shown) of the valve housing 12. A further, second connection line 78 is provided on the underside of the valve housing 12, extending in an axial direction parallel to the connection line 76, which second connection line discharges, with one free end thereof, into the tank connection T, and with the other free end thereof into the fourth fluid chamber 60. In addition, there are transverse branch lines 80, 82, which originate at the connection line 78 and which, on the one hand, discharge via the branch line 80 into the working spring chamber 84 in which the working spring 74 extends, and on the other hand, discharge via the branch line 82 in the direction of the third fluid chamber 44, wherein, when the valve is in the cold operating state according to the depiction in FIG. 1, the piston component 54 of the choke piston 50 completely covers said second branch line 82.
As is further shown in FIG. 1, an adjustment cylinder 86, which is designed as a differential cylinder, is connected to the valve 10, which will be explained in greater detail below, wherein the piston 88 of the adjustment cylinder 86 separates a piston chamber 90 from a rod chamber 92 in a conventional manner within the cylinder housing such that said separation is fluid-tight. A return spring 96 is provided within the rod chamber 92, through which a control rod 94 passes, which, in turn, is preferably actuated by the piston 88, as an integral component thereof, which return spring seeks to move the piston 88 in the direction of the unloaded state of said spring, from right to left as viewed in the direction shown in FIG. 1. The control rod 94, which is designed as a piston rod, in conjunction with the adjustment or variable displacement cylinder 98, forms the adjusting device (pivot angle SW) of a variable displacement pump 98, which may be designed as an axial piston machine, for example. An electric motor 100 may serve as a drive for the variable displacement pump 98, which may be a fixed displacement motor, but may also be a variable speed motor. Instead of an electric motor, another drive source may also be used. For the purpose of the functional description of the regulation, it is assumed that the pump has a constant drive speed, wherein this is not necessarily a requirement in actual operation. The variable displacement pump 98 removes the hydraulic fluid from the tank T and can supply this fluid at the end thereof, via a junction point 102, in the direction of the pump connection P, and thus supplies said fluid to a valve, wherein a screen or choke 106 is connected in said feed line 104 as a pressure differential or input choke. Starting at the junction point 102, the rod chamber 92 of the adjustment cylinder 86 is connected such that it can conduct fluid, and a hydraulic motor 108 is connected on the opposite side of the junction point 102, which motor serves as a fan drive and drives a fan blade 110 in the manner of a rotor. The fluid, which is transported from the variable displacement pump 98 through the hydraulic motor 108 then runs out on the tank side T. The volume of air flow, which is generated by the fan blade 110 in a conventional manner, flows through a heat exchanging device 112, which may be designed as a plate heat exchanger, for example, to which a hydraulic circuit 114 is connected, which serves to actuate a hydraulic work device, which is not depicted in greater detail here, for example, in particular in order to cool the fluid of said hydraulic circuit, which is transported through the exchanging device 112 by means of an additional pump device, which is not depicted in greater detail here. The hydraulic circuit 114 may be connected on the input side to the first fluid port 22, and on the output side to the second fluid port 24, of the valve 10 via fluid passages, which are not depicted in greater detail here; it is also possible to reduce the temperature in a separate fluid circuit, via the first and second fluid port 22 and 24, which circuit only indirectly reflects the operating temperature situation in the hydraulic circuit 114. In addition to these above-mentioned fluid passages, the piston chamber 90 of the adjustment cylinder 86 is connected to the working connection A via an additional connection line 116.
Before explaining the function of the valve solution shown in greater detail, it should be noted that, for a practical function, the compression spring 40 in the second fluid chamber 28 may also be omitted, and that, shown in a basic depiction, a damping choke 118 is connected in fluid communication between the utility connection A and the tank connection T within the valve housing 12. The fluid chamber 28 should be discharged towards the tank side T, which is not depicted.
In order to explain the manner of functioning, reference is first made to FIG. 4, which shows the valve 10 and the associated hydraulic system in an inactive operating state. As such, the system pressure is p0=0, because when the drive motor or electric motor 100 is switched off, the drive speed of the actuating pump 98nAn=0. As shown in FIG. 4, as such, the variable displacement pump 98 is adjusted to a full volume flow rate thereby, which is to say, the pivot angle SW of the variable displacement pump 98 is maximized. The control piston 30, which is designed as a differential area piston, is thereby held in the right-hand A-T position by the working spring 74, so that the working connection A, and thus the piston chamber 90, of the actuating cylinder 86 are connected to the tank connection T. Due to the tank connection to the piston chamber 90 that is created, the piston 88, which is guided in the actuating cylinder 90, is held in the position thereof that corresponds to the maximum pivot angle SW by the return spring 96. It is not imperative for the function thereof that the return spring 96 be present in the actuating cylinder 86, since actuating systems can certainly be implemented without a spring return. Moreover, there is a permanent connection between the working connection A and the tank connection T via the connection formed in the valve housing 12 via the damping choke 118. The travel distance S=min of the actuating element 64 of the thermal element 62 as well as the force F=min that is exerted on the choke piston 50 are minimized, optimally such that they equal zero, in accordance with the minimum temperature TFluid=m of the fluid.
Consequently the position of the control piston 30 remains substantially unchanged as the A-T position thereof. On the side allocated to the thermal element 62, in an inactive operating state, the choke piston 50 lies at a limit stop 58 (s. FIG. 5) in the form of a reduction in diameter in the interior of the valve housing 12.
If the system is brought from the inactive state into the active operating state, the variable displacement pump 98 is driven at a nominal speed nAN. Due to the fact that the fluid is still cold, essentially no force F=f(Smin) is exerted on the choke piston 50 via the thermal element 62, so that this choke piston separates the connection lines 76 and 78 from one another via the closed control edge. The system pressure p0, which builds up at the supply connection P is thus not lowered via the connection line 76 and therefore is exerted at a specifiable intensity on the differential pressure surfaces of the control piston 30, which is moved against the working spring 74 by the total hydraulic force that arises, and as a result, the P-A connection is opened, as shown in FIG. 1. The volume flow rate, which results from the pressure gradient between the supply connection P and the working connection A, together with the adjustment piston 88, formed on the differential piston, exerts a force on the large piston surface. If this force exceeds the action of force of the annular piston surface, which is subjected to pressure on the side of the piston rod, and which is thus the smaller annular piston surface, the adjustment piston 88 is displaced in the direction of the end position thereof that is on the right as depicted in FIG. 1. As a result, the volume of the adjustment cylinder 86 on the side of the piston rod is initially brought to a minimum, whereby the displacement volume of the variable displacement pump 98 is first reduced to a minimum, in that the piston 88 of the actuating cylinder 86 modifies the pivot angle SW towards smaller values.
The self-adjusting system pressure p0 substantially corresponds to the sum of the forces from the relatively weak preloaded working spring as well as the necessary actuating forces of the pump adjustment mechanism and ideally falls below the minimum pressure required by the driving hydraulic motor 108 in order to start up the fan 110. In the case of a fluid, which has a low temperature, the actuating element 64 of the thermal element 62 is at the minimum adjustment length thereof, which is to say, it is fully retracted. Fmin is the force that results from the minimum adjustment length, which force is exerted on the choke piston 50, and which can be assumed to be approximately zero, when the fluid is in a cold state, not otherwise specified. For the choke piston 50, this means that, in the case that the fluid is cold, said piston does not change its position with respect to the position thereof in the inactive operating state according to FIG. 4, so that the lines 76 and 78 are separated from one another by the closed control edge, as described above. A change in the state only occurs as a result of an increase in temperature.
This state is depicted in FIG. 5. There is an increase in the travel distance of the thermal element 62 or, respectively, of the actuating element 64 thereof and a corresponding displacement of the choke piston 50 in accordance with the increasing temperature TFluid of the fluid.
The travel distance-temperature graph of the thermal element 62 shown in FIG. 2 is intended to clarify the function of the thermal element 62, and shows a first range, having a regular travel distance Sreg, which increases with a first slope, here, nearly 1, in a linear manner with the temperature Tfluid of the fluid, and an adjoining second range with an irregular travel distance Sover, which increases with a second slope, which is reduced as compared to the first slope, in a linear manner with the temperature TFluid of the fluid up to a maximum value. The regular travel distance Sreg thereby corresponds to a movement of the thermal element 62 or the actuating element 64 thereof in the control range, and accordingly, the irregular travel distance Sover corresponds to an excess movement of the thermal element 62 or the actuating element 64 connected thereto.
A displacement of the choke piston 50 occurs in accordance with the extension of the travel distance of the actuating element 64 of the thermal element 62, so that an increased initial load is exerted on the control piston 30 via the working spring 74. The increased force of the working spring 74 moves the control piston 30 in FIG. 5 to the right, as a result of which the control edge on the piston component 36 increasingly reduces the P-A fluid connection from the supply connection P to the working connection A and further, to the piston chamber 90 of the actuating cylinder 86, as a result of which a movement of the piston 88 of the actuating cylinder 86 increasingly increases the pivot angle SW of the variable displacement pump 98 in order to increase the displacement volume accordingly. At the same time, the choke piston 50 increasingly opens the connection between the connection line 76 and the second connection line 78, which runs to the tank connection T, using the control edge located on the piston component 54. As a result, the control pressure that is exerted upon the control piston 30 behind the input choke 106 in the fluid chamber 26 is lowered, which means that the system pressure p0 that exists on the pressure side of the variable displacement pump 98 must increase disproportionately in order to maintain the balance of forces at the control piston 30. As is made clear in FIG. 3, what is actually a linear pressure-temperature characteristic curve is thereby made non-linear, and instead, is adapted to the increasing characteristic curve of the fan, which increases cubically: see FIG. 3. Here, the working point of the inactive system is indicated as I, the working point of the active system in the case that the fluid is cold, is indicated as II, and a working point within the control range in the case that the fluid is warm is indicated as III. As can be seen, as compared to a control pressure P1, which corresponds to the linear pressure 50, an additional pressure P2 is needed in order to maintain the control pressure prevailing in the control range due to the reduction in pressure via the choke piston 5. As the temperature of the fluid increases, there is a corresponding increase in the system pressure P0 with a corresponding increase in the fan speed generated by the hydraulic motor 108.
FIG. 6 shows an operating state, in which the system pressure P0 has increased to a value, which corresponds to an overload state. The pressure that prevails here in the fluid chamber 26, and which is exerted on the control piston 30, generates a piston force that is directed towards the left, as depicted in FIG. 6, of an intensity, at which the stop element 48 (see FIG. 1) of the piston is brought into full contact with the choke piston 50 or, in other words, rests against the choke piston 50 so that the pressure is exerted on the actuating element 64 via the choke piston 5 and is therefore exerted on the thermal element 62. An overload of the thermal element 62 is avoided, however, in that the additional spring 68, which supports the thermal element 62, serves as an overload protection, which allows a yielding movement of the thermal element 62. At the same time, in the case that the position of the control piston 30 corresponds to the overload state, the P-A connection on the valve housing 12 is virtually un-choked, so that for a pressure cut-off, the piston 88 of the actuating cylinder 86 is moved in order to move the pivot angle SW of the actuating pump 98 in the direction of a minimum displacement volume and as a result, to create a pressure cut-off. In FIG. 3, the working point in the case that an overload state is reached is indicated as IV on the pressure-temperature characteristic curve.
FIGS. 7 through 9 show a second exemplary embodiment. This second exemplary embodiment differs from the first in that an internal fluid feed is provided in the valve housing 12 via a fluid line 27 from the supply connection P to the port 22 on the thermal element 62, and from said port, via a return line 29 to the second connection line 78, and therefore to the tank connection T. Since, in this way, an internal flushing fluid line is provided for the fluid, which defines the temperature of the thermal element, it is alternatively possible to omit the thermal element on the external port 22, as is shown in the drawing. In this respect, the internal fluid connection represents an alternative to the external port in the event that it is desired that the fan drive operate in a completely self-sufficient manner. The internal fluid line 27 is connected to the supply connection P via an input choke 31, and a second input choke 33 is located between the supply connection P and the fluid chamber, which second input choke is adjacent to the piston component 38. A further difference as compared to the first example is that a separation of the control fluid and actuating fluid is formed behind the supply connection P in that the control piston 30 has an intermediary piston component 35 between the piston component 38 at the end and the piston component 36, which intermediary piston component has the same effective piston surface as the piston component 36. A fluid branch 37, which branches off from the supply connection P, discharges into the fluid chamber 26 between the piston component 36 and the intermediary piston component 35. Because of this separation between the control pressure, which is operative in the fluid chamber 26 as a control force on the control piston 30, and the actuating pressure, which is exerted at the working connection A via the fluid branch 37 that branches off, in a manner that is controlled by the piston component 36, the possibility to work with a control pressure, which falls below the required minimum actuating pressure of the adjustment cylinder 86, is made available. A correspondingly lower control pressure having lower required spring rates at the control piston 30 allows for a low control oil consumption, and to this extent, a reduced loss in the level of efficiency at the control valve.
Apart from that, the manner in which the second exemplary embodiment functions corresponds to that of the first exemplary embodiment, so that this need not be addressed in greater detail here.
Patent Application
20150308468
